JPS6323639Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention is a hydraulic control device for an automatic transmission, more specifically, it is possible to switch to each range such as parking, neutral, drive, reverse, etc. by operating a manual valve housed in a valve body, and in the drive range. The present invention relates to a hydraulic control device for an automatic transmission that can automatically switch between low gear and high gear.

Generally, this type of automatic transmission is equipped with a shift valve combined with a governor, and the shift valve controls the supply of pressure oil to the drive actuator and low servo actuator of the automatic transmission. The drive range is designed to automatically switch to low gear or high gear.

By the way, when converting a so-called semi-automatic automatic transmission, which does not have a mechanism for switching between low gear and high gear in the drive range as described above, to a full automatic transmission, a shift valve combined with a governor may be incorporated into the valve body, or A solenoid valve that operates according to the vehicle speed and the opening degree of the throttle valve may be installed in the oil path, but even if the shift valve is incorporated, it is not necessary to form a valve hole for the shift valve in the valve body. Or, it is necessary to make fundamental improvements such as changing the configuration of the oil passage formed in the valve body.Also, even if a solenoid valve is installed, it is necessary to secure a place to install the solenoid valve, and furthermore, it is necessary to make a fundamental improvement such as changing the configuration of the oil passage formed in the valve body. It was necessary to newly form a valve seat on the road, which was a factor in increasing the overall cost.

The present invention was devised in view of these circumstances, and its purpose is to provide an automatic transmission that allows the semi-automatic automatic transmission described above to be used as a fully automatic automatic transmission with extremely simple modification. The purpose is to provide a hydraulic control device for a machine.

That is, the valve body plate interposed between the transmission case and the valve body is provided with an orifice hole for controlling the supply of pressure oil to the drive actuator and the lower servo actuator. In this invention, a switching valve having a ball-shaped valve body operated by a solenoid is provided in the first oil passage, and an orifice hole for throttling is provided in the valve body plate in the middle of the first oil passage. A seat surface of the valve body of the switching valve is formed in the orifice hole, and the actuator side of the switching valve in the first oil passage is opened by opening the orifice hole by the operation of the valve body. It is connected to the discharge side of the pump via a manual valve, and connected to the suction side of the pump when the orifice hole is closed by the operation of the valve body, so that low gear and high gear are automatically shifted in the drive range. This makes it possible to switch between them.

DESCRIPTION OF THE PREFERRED EMBODIMENTS A hydraulic control device for an automatic transmission according to the present invention will be described below with reference to embodiments shown in the drawings.

The embodiment shown in the drawings is used for an automatic transmission that can shift in four stages: parking range, reverse range, neutral range, drive range, and low range. The planetary gear system includes a drive clutch, a reverse clutch, and a brake band that performs a low servo action, and each of the clutches and brake band is interlocked with an actuator consisting of a cylinder and a piston. It supplies hydraulic oil to the piston action side of the drive actuator A that operates the drive clutch, and to the low servo piston release side and the action side of the low servo actuator B that operates the brake band. Then, by opening the low servo, the planetary gear device is placed in a high gear state, and hydraulic oil is supplied only to the low servo piston action side of the low servo actuator B, and the low servo is operated. The planetary gear system is set to a low gear state, and hydraulic oil is supplied to the piston acting side of the reverse actuator C to set the reverse state, and each of the actuators A, B,
By cutting off the supply of hydraulic oil to C and opening it to the tank, it is brought to a neutral or neutral state.

In the figure, 1 is an oil pump, 2 is a pressure regulator valve, and 3 is a manual valve operated by the operation of the control lever 18, and the pressure regulator valve 2 is of the 4-land type. A spool 21 and a spring 22 branch from the discharge passage 11 of the oil pump 1 between the back chamber 23 and between the first and second lands 21a, 21b and between the second and third lands 21b, 21c. The branch passage 12 is connected to the first and second lands 21a, 2.
1b, an oil supply passage 6 for supplying oil to the torque converter 5 via an orifice 4 is connected to the valve 2, and the third land 21c is connected to the valve 2.
The third and fourth lands 2
The branch passage 12 is connected to the connecting passage 1 between 1c and 21d.
2a, and in the middle of this connection passage 12a, an electromagnetically actuated type that closes the passage 12a and releases the pressure oil introduced between the third and fourth lands 21c and 21d into the drain passage 13. A pressure regulating switching valve 7 is provided, and the operation of the switching valve 7 enables the pressure regulating control by the pressure regulator valve 2 to be adjusted in two stages.

That is, the diameters of the lands 21a to 21d are such that the first and second lands 21a and 21b have the same diameter, and the third land 21c has a larger diameter than the fourth land 21d, and the pressure regulation switching When the connecting passage 12a is closed by the operation of the valve 7, the hydraulic pressure of the pump 1 is regulated to a low pressure of, for example, 4 kg/cm ² only by the elastic force of the spring 22, while the pressure regulating switch is When the valve 7 is OFF and pressure oil is introduced between the third and fourth lands 21c and 21d, the elastic force of the spring 22 causes the third land 21c and the fourth land 21d to
The force obtained by adding the pressing force due to the hydraulic pressure acting on the area difference of is made to oppose the force due to the hydraulic pressure acting on the first land 21a, and the hydraulic pressure of the pump 1 is regulated to a high pressure of, for example, 8 kg/cm ² . It is.

The manual valve 3 uses a four-land type spool 30, and one end of the spool 30 in the length direction is provided with five detent grooves 31, 32, corresponding to the parking range and four shift ranges. 33, 34, and 35, and the rightmost detent groove 31 in the drawing
is the daytent groove corresponding to the parking range, and the daytent groove 3 is arranged toward the right side.
Detent grooves 2 to 35 correspond to reverse range, neutral range, drive range, and low range, respectively.

The pressure regulator valve 2 and the manual valve 3 are housed in a valve body 81 that is attached to the transmission case 8 via a valve body plate 80, as shown in FIG. A housing hole 81 for the pressure regulator valve 2 is provided in the valve body 81.
a and a housing hole 81b for the manual valve 3, and a stopper 81c that engages with the detent grooves 31 to 35 of the manual valve 3 to position the spool 30 is provided.

Further, the valve body 81 and the transmission case 8 are provided with a first oil passage 41 that communicates with the piston action side of the drive actuator A and the piston release side of the low servo actuator B.
and a second oil passage 42 communicating with the piston action side of the low servo actuator B, a third oil passage 43 communicating with the piston action side of the reverse actuator C, and drain oil communicating with the tank T. return oil passages 46, 47 which form the passages 44, 45, branch from the first oil passage 41 and the third oil passage 43, and are connected to the tank T through the accommodation hole 81b of the manual valve 3; A return oil passage 48 is formed which branches from the second oil passage 42 and is connected to the accommodation hole 81b.

Further, the first to third oil passages 41, 42, and 43 are provided with throttling mechanisms 41a, 41b, and 41c, respectively.
a, 41b, 41c are formed by orifice holes 82 formed in the valve body plate 80.

On the other hand, in the middle of the first oil passage 41, there is provided a switching valve 9 for automatic transmission that switches the oil passage 41 between the discharge side and the suction side of the pump 1 in the drive range, and the switching valve 9 is turned ON. When activated, the actuators A and B sides of the switching valve 9 in the first oil passage 41 are connected to the drain passage 13 leading to the suction side of the pump 1, and the low servo actuator B connects the actuators A and B sides of the switching valve 9 to the drain passage 13 leading to the suction side of the pump 1, and the low servo actuator At the same time, the gear is switched to a low gear, and the actuator A, B side of the switching valve 9 in the first oil passage 41 is connected to the discharge passage 11 of the pump 1 by turning off the switching valve 9, and the low servo is released. , by operating drive actuator A, the planetary gear of the automatic transmission is to be switched to a high gear.

In the embodiment shown in the figure, the switching valve 9 for automatic transmission includes a ball-shaped valve body 90 operated by a solenoid 91, and a valve body 90 between the first oil passages 41 provided in the valve body plate 80. A seat surface 82a of the valve body 90 is formed in the orifice hole 82, and by opening the orifice hole 82 by the valve body 90, the actuator A, B side of the switching valve 9 in the first oil passage 41 is opened. The actuator A, B side of the switching valve 9 in the first oil passage 41 is connected to the discharge passage 11 of the pump 1 via the manual valve 3, and the actuator A, B side of the switching valve 9 in the first oil passage 41 is connected to the suction of the pump 1 by closing the orifice hole 82 by the valve body 90. The drain passages 13 are connected to the drain passages 13 leading to the sides.

That is, in the embodiment shown in the figure, a valve case 95 is attached to a housing 94 containing a solenoid 91 and a movable core 92 as shown in FIG.
The movable iron core 92 and the push rod 93 integrally formed with the iron core 92 are installed in the valve hole 95a of No.
Furthermore, a port 97 is provided on the side wall of the valve case 95 to connect the valve hole 95a to the drain passage 13.

On the other hand, a mounting hole 8a communicating with the first oil passage 41 is formed in the side wall of the transmission case 8, and the valve case 95 is screwed into the mounting hole 8a. Valve seat 9
6 and a seat surface 82 a formed in the orifice hole 82 of the valve body plate 80 .

Further, in the embodiment shown in the figure, the pressure regulating switching valve 7 is also constituted by a ball-shaped valve body 70 operated by a solenoid 71, and like the automatic transmission switching valve 9, a fourth valve body 70 is provided. As shown in the figure, a valve case 75 is attached to a housing 74 containing a solenoid 71 and a movable iron core 72.
The movable iron core 72 and the iron core 72 are inserted into the valve hole 75a of the
A push rod 73 integrally formed with the valve hole 75 in the valve case 75 is installed inside the valve case 75.
The valve seat 76 of the valve body 70 is provided on the opening end surface of the valve case 75, and the valve hole 75 is provided on the side wall of the valve case 75.
A port 77 is provided to connect the drain passage 13 to the drain passage 13.

A mounting hole 8b communicating with the connection passage 12a is formed in the side wall of the transmission case 8, and the valve case 75 is screwed into the mounting hole 8b. The seat surface 8 of the valve body 70 is inserted into the orifice hole 83 formed in the body plate 80.
3a, and between this seat surface 83a and the valve seat 76 formed on the valve case 75, the valve body 7
0 is inserted.

Further, the pressure regulating switching valve 7 and the automatic transmission switching valve 9 are configured to operate according to the vehicle speed and the opening degree of the throttle valve.

That is, the pressure regulating switching valve 7 is configured to switch the line pressure between, for example, 4 kg/cm ² and 8 kg/cm ² based on the range shown in FIG. 5 in relation to the vehicle speed and the throttle opening. For example, the throttle opening is 1/4
When the vehicle speed is 40 km/h, the pressure regulating switching valve 7
When the solenoid 71 is energized, as shown in FIG. 2, the valve body 70 is moved to the left in the figure via the movable core 72 and the push rod 73, thereby closing the connection passage 12a. The pressure oil between the third and fourth lands 21c and 21d in the pressure regulator valve 2 is released to the drain passage 13, thereby regulating the oil pressure of the oil pump 1 to 4 kg/ ^cm2. On the other hand, for example, when the throttle opening is 2/4 and the vehicle speed is 10 km/h, the power to the solenoid 71 is cut off and the valve body 70 is closed to the connecting passage as shown in FIG. 12a moves to the right in the figure to open the connection passage 12a, and at the same time, the connection passage 12a opens.
and the drain passage 13 is cut off.
As a result, the oil pressure of the oil pump 1 is 8 kg/
It is regulated to ^cm2 .

In addition, the automatic transmission changeover valve 9 has a sixth position in the drive range in relation to the vehicle speed and the throttle opening.
When switching between a low gear and a high gear in the range shown in the figure, for example, when the throttle opening is three-quarters and the vehicle speed is 10 km/h, the solenoid 91 of the automatic gear changeover valve 9 is activated. When energized, the valve body 90 is moved to the left in the figure as shown in FIG. 1, and the actuator A, B side of the switching valve 9 in the first oil passage 41 is connected to the drain passage 13. As a result, the low servo is operated via the low servo actuator B, and the gear is switched to the low gear. On the other hand, for example, when the throttle opening is 1/4 and the vehicle speed is 40
Km/h, the energization to the solenoid 91 is cut off and the valve body 9 is turned off as shown in FIG.
0 is from the oil pump 1 to the manual valve 3
is moved rightward in the figure by pressure oil sent through the valve, and connects the actuator A, B side of the switching valve 9 in the first oil passage 41 to the discharge passage 11 of the oil pump 1; As a result, the drive actuator A operates, the low servo is released, and the gear is switched to high gear.

In the drawing, D is an accumulator, E is an oil cooler, and F is a lubricating part of the engine.
It is connected to the return passage 14 from the torque converter 5.

Further, 15 is a vehicle speed detector, 16 is a throttle opening detector, 17 is a switch that is turned on when the control lever 18 is shifted to the drive position, and 19 is a vehicle speed signal from the vehicle speed detector 15 and a throttle opening detector. This is a microcomputer that controls on/off the switching valves 7 and 9 based on the throttle opening signal from the throttle angle detector 16.

As described above, in the present invention, a switching valve equipped with a ball-shaped valve body operated by a solenoid is provided in the first oil passage, and an orifice hole for throttling is provided in the valve body plate in the middle of the first oil passage. A seat surface of the valve body of the switching valve is formed in the orifice hole, and the actuator side of the switching valve in the first oil passage is opened by opening the orifice hole by the operation of the valve body. connected to the discharge side of the pump via a valve;
In addition, the orifice hole is closed by the operation of the valve body to connect to the suction side of the pump, and in the drive range, it is possible to automatically switch between low gear and high gear by the operation of the switching valve. It is possible to convert a semi-automatic automatic transmission into a fully automatic transmission by making extremely simple modifications without changing the oil passage configuration formed in the valve body and transmission case.

[Brief explanation of drawings]

The drawings show one embodiment of the present invention. Figures 1 and 2 are piping system diagrams showing the operating states of the automatic transmission changeover valve and pressure regulation changeover valve in the drive range, and Figure 3 is the hydraulic control system of the present invention. Fig. 4 is a partially cutaway side view of the main parts, and Fig. 5 is a partially cutaway side view of the automatic transmission incorporating the pressure regulating valve. Pressure diagram, FIG. 6 is an automatic transmission diagram showing the operating range of on/off operation of the automatic transmission switching valve. 1... Oil pump, 2... Pressure regulator valve, 3... Manual valve, 7...
Pressure regulation switching valve, 8...transmission case,
80... Valve body plate, 81... Valve body, 9... Automatic speed changeover valve, 90... Valve body, A... Drive actuator, B... Low servo actuator.

Claims (1)

[Scope of utility model registration request] The valve body is assembled to the transmission case via the valve body plate, and by switching the manual valve housed in the valve body to the drive range, the oil pump discharge side is connected to the piston action side of the drive actuator and the low servo actuator. A first oil passage communicating with the piston open side of the yuator and a second oil passage communicating with the piston acting side of the low servo actuator are connected to switch to a high gear and shift the manual valve to a low range. In the hydraulic control device for an automatic transmission, the first oil passage is opened to the tank and the second oil passage is connected to the discharge side of the oil pump to switch to a low gear by a switching operation of the solenoid. A switching valve equipped with a ball-shaped valve body that operates by is provided in the first oil passage, and an orifice hole for throttling is formed in the valve body plate in the middle of the first oil passage. A seat surface of the valve body of the switching valve is formed on the valve body of the switching valve, and the actuator side of the switching valve in the first oil passage is opened by opening the orifice hole by the operation of the valve body, and the valve body of the switching valve is opened through the manual valve. A hydraulic control device for an automatic transmission, characterized in that it is connected to a discharge side, and connected to a suction side of the pump when the orifice hole is closed by the operation of the valve body.